Variable speed mechanism



Dec. 3, 1940. s, Q Wi 2,223,711

VARIABLE SPEED MECHAN I SM Original Filed Dec. 10, 1935 4 Sheets-Sheet l ENVENTOR 5.1% C. Mhyer ATTGRNEY Dec. 3, 1940. s, Q wlNGER 2,223,711

VARIABLE SPEED MECHANI SM Original Filed Dec. 10, 1935 4 Sheets-Sheet 3 FIG. 6. Fm} as BNVENT'QR I C? b A TORNEY Dec. 3, 1940. s Q wlNGER 2,223,711

VARIABLE SPEED MECHANIC SM Original Filed Dec. 10, 1955 4 Sheets-Sheet 4 l N V E' N T O R .Efarc-r C. Myer BYW M ATTORNEY Patented Dec. 3, 1940 UNITED STATES VARIABLE SPEED MECHANISM Stover C. Winger, Los Angeles, Calif., assignor to Guy H. Hall, Los Angeles, Calif.

Application December 10, 1935, Serial No. 53,806 Renewed April 6,1940

21 Claims.

This invention relates to a device for transmitting motion or power from one element to another. More particularly, it relates to a device that can be adjusted for varying speed ratios,

through a continuous range.

It has been proposed in the past to utilize for this purpose, a planetary drive, in which one wheel is stationary and the other is arranged to roll on the periphery of the fixed wheel, the effective diameter of at least one of the wheels being variable. In this way the rate of angular motion of the planetary wheel about its own axis is made variable also.

It is one of the objects of this invention to improve in general on planetary drives of this character.

In particular, a device constructed in accordance with the present invention is so arranged that the driving contact between the members is on the side surfaces thereof'instead of the periphery.. The surfaces are urged together in such manner that the contact areas in driving relationship are limited selectively in succession to the area at and neighboring the common tan- 25 gent to the circles corresponding to the effective diameters of the two wheels in planetary driving relation.

By limiting this area of contact not only to this locality but also to the side surfaces of the members, it is seen that it is possible to enlarge the effective diameter of the circle corresponding to the planetary wheel, even beyond the diameter of the stationary wheel, and even when the planetary action can be described as taking place on the concave side of the circle corresponding to the stationary wheel.

It is accordingly another object of this invention to make it possible to secure these results, and especially by the aid of simple and inexpensive apparatus. I

In particular, the elements required to accomplish the desired effects include one-way drives such as pawl or ratchet drives; but for practical use, rolling wedge elements are utilized. These 45 rolling wedges may be in the form of balls or rollers. They are preferably arranged in an annular band around the center of one or the other of the wheels, andv are quite closely spaced in an angular direction. The wedging spaces are so arranged that the direction of drive can be made selective to determine the direction of rotation of the driven shaft. Thus a change in the wedging direction determines at which of two diametrically opposite points a driving contact can be established; these two points progressing in succession in accordance with the angular progression of the planetary wheel. It will be seen later on, that these points lie on the extremities of a diameter drawn through the two axes of the two wheels.

It is accordingly still another object of this invention to provide this type of unidirectional drive between wheels corresponding to a planetary drive.

One advantageous effect of a drive of this con- 10 struction is that it provides a free wheeling effect similar to that used for automobile drives by an overrunning clutch device. It is therefore still another object of this invention to secure this effect in a compact mechanism capable of 15 being used as either a clutch or speed change device for vehicles. Since the change in speed is .a continuous function of the change in effective relative diameters of the wheels, the change speed is smooth in operation.

It is still another object of the invention to provide a simple and improved control means for the speed change, involving a mechanism for varying the spacing between the axes of the-two wheels, and for compensating for the unbalance due to the eccentric motion of the planetary wheel.

Since the planetary wheel is caused to rotate at varying speeds about its own axis to secure the desired speed variation, itis necessary to provide a universal drive from the axis of the planetary wheel to the drive shaft. It is another object of this invention to provide .an improved power connection of this character.

This invention possesses many other advantages, and has other objects which may be made more easily apparent from a consideration of one embodiment of the invention. For this purpose there is shown a form in the drawings accompanying and forming part of the present specifi- 40 cation. This form shall now be described in detail, illustrating the general principles of the invention; but it is to be understood that this detailed description is not to be taken irr a limiting sense, since the scope of the invention is best defined by the appended claims. 7

Referring to the drawings:

Figure 1 is a vertical sectional view of a transmission incorporating the transmission, the setting being such that the speed ratio is infinity;

Fig. 2 is a cross-sectional view on an enlarged scale taken along plane 2-2 of Fig. 1;

Figs. 3, 4 and 5 are detail sectional views taken along correspondingly numbered planes of Fig. 2;

Figs. 6, 7, 8, 9, 10 and 11 are detail sectional views taken along correspondingly numbered planes of Fig. 1;

Figs. 12, 12a, 13, and 13a are diagrams illustrating the mode of operation of the transmission under various operating conditions; and

Fig. 14 is a diagram illustrating the mode of operation of the driving connection to the driven shaft. 3

In the present instance the member which forms the equivalent of a planetarycr rolling wheel is provided by a flat disc or plate I6. This disc I6 is splined to a shaft 39. In the positions shown in Figs. 1 and 2 the eccentricity of shaft 39 with respect to a driving shaft is zero; but

15 as will be described hereinafter, this eccentricity can be increased to a definite value so that the spacing of the axes of shaft 39 and of shaft I can be adjusted,

It is sufficient for the present to note that shaft '39 is guided for angular motion about its own axis partly by the aid of an extension 40 and a stub shaft 4|, over which extension the right hand end of shaft 39 is joumalled. For this purpose the right hand end of shaft 39 has a recess or aperture I00.

The equivalent of a stationary wheel upon which the planetary rolling is produced by the motion of disc I 6, is formed by a pair of stationary structures. Each structure includes a stationary plate l1, and elements such as 21, which serve to clutch the disc or plate l6 to the stationary members H at a restricted area, said area successively changing in position whereby the rolling planetary effect is secured. In the present instance these clutching members are represented by rolling elements 21 in the form of balls. The arrangement is such that these balls wedge between the stationary members I1 and the intermediate disc l6 for one direction of relative motion, and are freed from wedging action for the opposite direction of motion. It is also apparent therefore that there is obtained a rolling action by the aid of areas in contact between the balls 21 and the disc I6, in which the areas of contact lie in a plane substantially perpendicular to the axis of the member I6. I

As shown most clearly in Fig. 2, the balls 21 are arranged in an armular band around the axis of shaft I and are quite closely spaced in an angular direction. Thus as disc I6 is given its planetary motion by appropriate means to be hereinafter described, the localized area of driving contact imparting angular rotation of disc l6 about its own axis changes from one ball 21 to the next.

The manner in which the wedging spaces for the balls 21 are provided will now be described. In this connection Figs. 2, 3 and 4 show this construction most clearly. On-those sides of the stationary members I1, which are adjacent the disc l6 there are provided a series of pockets, formed in a slightly raised face of the members 11. The number of these pockets correspond with the number of the balls 21. Each of the pockets is formed by sloping sides 22 and 23. These sloping sides form a deep central portion for the pocket and two wedging spaces on each side of the central portion. Let it be assumed for example, that disc |6 is being moved in a clockwise direction by its planetary motion as represented by the arrow at the left of Fig. 4. For that direction of rotation, and when the balls 21 are Positioned as shown in that figure, it is seen that these balls become wedged in the converging spaces formed by the sides of disc I6' and the sides 22 of the pockets. Accordingly, for this position, the disc it will be rstrained at the area of contact between the balls 21 and the disc I6. The result is a counterclockwise rotation of disc it about its own shaft 39. 5

The direction of the pockets 22-23 is such as to be substantially tangential to the circle about which the balls 21 and the pockets 22-23 are arranged. Also as shown most clearly in Fig. 1, the disc It even for its, maximum possible eccenl0 tricity would still be in contact with all of the balls 21, although only a limited number actually restrain the motion of the disc. The manner in which the balls act to provide successive driving contact points will be hereinafter described. 15

Means are provided for simultaneously moving all of these balls so that they are all in wedging relation with the corresponding surface 4 22 or surfaces 23 of the pockets.

The mechanism for obtaining this result in-.20 cludes. a pair of shift members 30 and 3|. These members 30 and 3| are accommodated in the space formed between the stationary members l1 and are generally circular in shape. They may be dowelled together as by the aid of sev- 25 eral pins 34 (Figs. 2 and 5), arranged in contacting bosses on these members. These members 30, 3| also have side flanges 3233 in sliding contact respectively with the inner surfaces of stationary members l1. They are guided for an- 30 gular motion about the axis of driving shaft l as by the aid of hollow tubes 20 which are pressed or otherwise held in central apertures formed in the members |1. Thus each of the members 3|] and 3| is provided with a central bore fitting over 35 the corresponding tube 29. Leading from the central bore are a number of radial slots 36. The number of these radial slots corresponds with the number of balls 21; and the balls are accommodated in these slots with considerable clearance. It is apparent that when the shift members 30 and 3| are angularly adjusted about the axis of shaft the balls 21 will be given a corresponding angular motion due to contact with the sides of slots 36, so as to shift them from one side 5 of the corresponding pockets to the other. Thereby a change in the wedging direction is obtained.

This angular shifting of members 30 and 3| can be provided by the aid of a radial handle 35, 50 having an inner threaded portion engaging one orthe other of the two members 36-3|. A slot 31 can be provided in the cylindrical casing 2 which houses the mechanism. The angular extent of the slot 31 cooperates with the shank extending from handle 35 to limit the throw of the shift members 30 and 3|.

Furthermore, the arrangement is such that the balls 21 are yieldingly held in one or the other side of the corresponding pockets 22-23. For this purpose each pocket is provided with a spring arm 26 located immediately above the deepest portion of the pocket. This spring arm is supported as by the aid of a shank 24 lying in groove 25 in the pocket and having a right angular 'ex- 5.

tension fitting into an aperture in the corresponding stationary member H. The spring arm 26 projects into the path of the'ball 21. As the shift arm 35 is rocked, the ball 21 snaps either to one side or the other of the spring arm 26 which is 70 momentarily depressed during, this shifting operation. It is thus seen that after the shift arm 35 is operated, all of the balls 21 are held against accidental dislodgment from the desired wedging position. u v

All of the balls 21 are thus retained consistently in wedging position for either a clockwise or a counterclockwise motion along the circumference of the circle Joining the centers of balls 21. It is also to be observed that since there are two sets of balls 21 on opposite sides of the disc or plate I3, the thrust occasioned by the wedging action on disc I6 is neutralized and there is no unbalanced force tending to move the shaft 38 in an axial direction.

The operation of the device can be best explained in connection with Figs. 12, 12a, 13 and 13a. In Fig. 12, the disc member I3 has its outside periphery indicated by dotted lines. The light line circle IOI corresponds to the circle passing through the centers of the pockets 22-23. The axis of the driving shaft I is indicated by the small circle I03; and the axis of disc I6 is indicated by the small square I04. It is assumed that in the position of Fig. 12 the balls 21 wedge for clockwise direction of motion' along the circumference of circle IOI. This condition is indicated by the position of the line 22 representing the corresponding slanting surface of pocket 2223. It is also assumed that the disc I6 is given a planetary motion in a clockwise direction as ind-icated by the arrow associated with the axis I04.

Although the diameter of disc I6 is that indicated by the dotted line, the effective diameter of the planetary wheel is that indicated by the heavy line I02 which is tangent internally of the circle IOI of the pockets 22-23. This can be realized immediately when it is appreciated that planetary driving contact can only occur at the circle I0 I, and the relative spacing of centers I03 and I04 determines the radius of circle I02. If R is the radius of circle IOI, and r the radius of circle I 02, the distance between the centers, as well as these radii fulfill the condition that the constant value R must equal the sum of the two variables 1' and the distance between the centers I03 and I04. The center I04 of'disc I6 in the instantaneous position of Fig. 12 as'in all the other diagrams, is represented as vertically above the center I03 of the stationary members I1.

Th planetary circle of contact I02 moves as a unit toward the right as viewed in Fig. 12. This is due to the planetary motion of disc IS in a clockwise direction. Accordingly, the surface of disc I3 wedges ball 21 in the top pocket, which pocket corresponds in-location to the point I 01, at the extremity of the diameter I05 passing through points I03 and I04. The ball 21 corresponding in position to the point I08 at the lower extremity of diameter I05 is not wedged by this action, because disc I8, moving towardthe right, tends to move ball 21 out of its pocket. Accordingly, the disc I 6 is confined at an area neighboring the point of tangency I01 between circles IBI and I02; disc I6 is not confined by any other of the balls. This is due to the fact that the balls which grip the disc I6 most strongly at any instant are those which correspond closest in space to the intersection I 01 of the line I05 with the circle I 0|, where the direction of disc motion is most nearly in line with the wedging direction. These wedging balls at these areas, one on each side of disc I6, are diagrammatically represented by the top ball 21 of Fig. 12. This point of contact thus serves as a stationary fulcrum about which the circle I02 must roll, and the direction of that rotation is counterclockwise, as indicated ping action is less strong than the gripping action In other words, although disc I6 is in contact with all of the balls 21 at all times, yet one only (in each of the two annular sets of balls) corresponding in space closest to the point I01, serves as a fulcrum restraining motion of translation of disc I6. Accordingly, disc I6 is rotated in a counterclockwise direction about the axis I04. Point I01 thus serves as a rolling point of contact, as in ordinary planetary gears. 01 course as the planetary motion proceeds, the line I05 moves in a clockwise direction about center I03, the balls 21 are in succession placed in the wedging position. The ultimate result is as if a planetary wheel I02 were rolling on an inner periphery of stationary wheel I 0|.

It can readily be demonstrated that the number of revolutions of planetary wheel I02 for each revolution of the axis I04 about axis I03 is equal to where R is the radius of circle IN and r is the radius of circle I02. It is thus seen that the greater the eccentricity, causing a reduction in the radius r, the faster the disc I6 will rotate in a counterclockwise direction. This provides an adjustable speed by varying the spacing of the two axes I03 and I04. When axis I04 is made concentric with axis I03 as represented in Fig. 1, the speed reduces to zero. This is also apparent from the formula given hereinbefore where the numerator of the formula reduces to zero, when the two radii R and r areequal.

The direction of rotation imparted to shaft 39 in this mechanism depends solely upon the position of the balls 21 in their pockets. Thus upon reversal of the rotation of drive shaft I, the direction of, rotation of disc I6 remains the same: however, the speed ratio is different.

This action is illustrated in Fig. 12a. In this case the axis I04 of the disc I5 is revolved in a counterclockwise direction. The ball 21 corresponding in position to the lower point I03 is now in wedging position, since the disc I6 is moving toward the left. The ball 21 corresponding in position closest to the point I01 is free. The effect is that the point I08 now forms a fixed fulcrum since it corresponds to the wedging ball. The result again is a. rolling of a circle I09 on circle I III. This circle I09, it is seen, is larger in diameter than the stationary circle IOI; but

since side contact only is provided for, betweenv I08, wedges toward the right. Thus if disc I6 is given a planetary motion in a counterclockwise direction as illustrated by the arrow associated with the axis I04, the point II acts as a fulcrum point and rotation of disc I6 is in the direction indicated by the'arrow III. This direction is clockwise.

The direction of rotation of disc I6 is again unaltered although the direction of the revolution of axis I04 be reversed. This is illustrated in Fig. 130., where the planetary motion now takes place in a clockwise direction. In this case the fulcrum point is at I08 and rolling of discs I6 remains in the clockwise direction but at a reduced ratio.

With this preliminary explanation of the mode of operation of the device, a more detailed description of various elements in the mechanism can now be set forth.

It is of course understood that the drive shaft I can be connected to any appropriate source of motion, such as a motor or engine. The main portions of the mechanism are enclosed in a casing or housing of general cylindrical form. This housing can be in sections and end plates 3 and 4 may be provided. These end plates have integrally supporting feet. Tie-bolts 5 serve to hold the end plates and the housing 2 in assembled position. These bolts, as shown most clearly in Figs. 1 and 2, pass through-the stationary members II and outside of the circumference of the shift members 303|. It is apparent that the bolts 5 thus serve accurately to center the members II with respect to the axis of shaft I. The shaft 5 represents the take-off shaft and is shown as coaxialwith shaft I.

The mechanism whereby a planetary motion is imparted to disc I6 will now be described. The drive shaft I is rotatably supported in any preferred manner as by ball bearings 44 and 45 secured in the hub 46 shown in this instance as integral with the end-plate 3. As indicated in Fig. 1, this drive shaft I projects outside of the mechanism for ready connection to a source of motion. The inner end of the shaft'is enclosed within the housing 2 and is provided with a cylindrical head 41 integral with the shaft. This head is shown to best advantage in Figs. 1, 6, 7 and 8;

Stub shaft 4|, supporting disc I6, is shown as integral with a slide 42, slidable in a wide transverse slot 48 in the head 41. This slide can be adjusted so as to vary the spacing of shaft 4| with respect to shaft I. In slot 48 is also slidably mounted a counterweight 40. These members 42 and 49 are in side contact as shown most clearly in Fig. 8, and are retained in the slot 48 as by the aid of the plates 50, which are secured to head 41 as by screws 5|. It is apparent that members 42 and 49 are independently slidable in the transverse slot 48.

The mechanism whereby the counterweight 49 and slide 42 are moved transversely of the slot 48 in opposite directions includes cams or eccentrics 54 and 55 (Figs. 6, '7 and 8). These eccentrics are axially displaced and operate respectively in slots 52 and 53 cut respectively in counterweight 49 and member 42, and having longitudinal axes transverse to the slot 48. The centers of eccentrics 54 and 55 are arranged 180 apart. A shaft 56, which carries the eccentrics 54, 55, is shown as coaxial with shaft I, and rotatably accommodated in a bore 51 in the inner end of drive shaft I.

The sides of slots 52 and 53 engage the periphcry-of the corresponding eccentrics 54 and 55. Therefore if shaft 56 be rotated with respect to shaft I from the position shown in the drawings, plate 42 with its stub shaft 4| will move to the left as viewed in Fig. 6; and correspondingly then counterweight 48 will move to the right as viewed in Figs. 6 and 'I. Since stub shaft 4| carries the projection 40 upon which the shaft 39 is supported, it is apparent that the relative angular position of shaft 56 with relation to shaft determines the distance between the axes of disc I6 and of stationary members I]. This in turn determines the effective diameter of theplanetary wheel I02 illustrated in Fig. 12.

The relative angular position of shafts I and 56 is adjusted by the aid of the mechanism illustrated most clearly in Figs. 1, 8, 9 and 11. Shaft I has a slot I3 therein, and shaft 56 has a slot I4 therein. Thesetwo slots are non-parallel. For example, slot I4 can be parallel to the axis of the shafts, and slot I3 can be helical with respect thereto. In order to adjust the angular positions of the shafts I and 56, use is made of a pin I2 which projects through slot I3 and into slot I4.

Due to the fact that the slots I3 and I4 are diver- 'to shift the collar 61, use is made of a ring 65 disposed between the flanges 68 and 69 of the collar 61. In order to permit collar 61 to rotate freely with the shaft I, ball thrust bearings I0 and II can be disposed between the ring 65 and the flanges 68-69. Axial movement of the ring 65 thus causes axial movement of the shift collar 61.

This axial movement of ring 65 is provided by the aid of a handle 6|. This handle is attached, as by the aid of a threaded portion, to an adjustable collar 60 on hub 46. The handle 6| carries the pin projection 63 which extends through a transverse slot 64, which may be in the form of a helix, cut in hub 46 and engaging'in the ring 65. The pin 63 also passes through a corresponding slot in the spacer sleeve 66 within the hub 46.

It is evident that when handle 6| moves collar 60 with respect to the groove 64, the shift member 61 will be moved in an axial direction. This in turn will cause a variation in the relative angular position of shafts I and 56. The relative angular position of shaft 56 determines the radial positions of eccentrics 53and 54 and thereby the radial position of stub shaft 4| and counterweight 49.

The mechanism for translating the rotation of disc I6 about its own axis to rotation of shaft 6- will now be described. This mechanism is desig- This plate also has a groove 82'of substantially semi-circular cross section, on its inner face.

Interposed between the two plates 18 and 8| is a third or coupling plate 83. It is provided on its opposite faces with grooves 84 and 85 respectively. The grooves 84 and 85 are transverse to each other; in the present instance they are shown as being perpendicular to each other. The grooves are definitely limited in radial extent on the intermediate plate 83 as by the abutments 81 and 88. Corresponding overhanging abutments are also provided at the extremities of the grooves 88 and 82.

Coupling the intermediate plate 83 to both plates 18 and 8| are a plurality of balls 88 and 88. Balls 88 are located in grooves 84 and 82 and balls 88 are located in grooves 88 and 85.

These balls 88 and 88 form virtually rolling keying members between the planetary mechanism and the shaft 8.

As shaft 38 rotates about an axis spaced from the axis of shaft 8, the intermediate plate 83 is constrained by balls 88 to adjust itself continuously (by movement along the axis of grooves 82 and 84) to keep grooves 88 and 85 in linear alinement. The effect is similar to that of a universal joint. Of course the maximum eccentricity between the axes is represented by the length of a radial groove, which is always less than the length of the radius of plate 83. The action is most clearly illustrated in the diagram of Fig. 14. In this figure, the heavy circle 8| represents the plate 8|v attached to the driven shaft 8; the light circle 18 represents plate I8 attached to shaft 38; and the dotted circle 83 represents the intermediate plate 83 interposed between the other two plates. 1 7

Assume that the plate 78 is in an eccentric position with respect to plate 8|, and that its axis H2 is revolving about axis H3 of plate 8|, and that for the instant shown, grooves 88 and 85 occupy a position indicated by line Ill. The center H8 of intermediate disc 83 must fall somewhere on line 4, due to its constraint by virtue of .the grooves. pass through the axis I I3 due to the constraint of grooves 82 and 84. Accordingly, this center 8 can be located by drawing a line 8 perpendicular to line 4 and passing through the center 3. sponds in direction to grooves 82 and 84, which are always perpendicular or transverse to grooves 88 and 88, represented by line 4.

It is apparent that rotation'of plate vI8 will cause a corresponding rotation of plate 8| due to the driving connections along lines 4, H8; and that this drivingconnection holds for any relative positions of axes H2 and 3. Although in the present instance but one ball is shownj in each radial portion '01 the grooves 84"and 88, it is apparent that several balls might be;

used.

A ball thrust bearing 88 can be interposed between the left hand face of plate 8| and a threaded bushing 8| that is mounted in the hub 82 of the end plate 4. This bushing 8| serves to maintain the plates I8, 8| and 83 against axial separation.

It is apparent from a consideration of Figs. 12, 12a, 13 and 1341., that an overriding clutch efiect is also provided by the mechanism. Thus in Fig. 12 if rotation of the wheel I82 occurs in a counterclockwise direction faster than it is driven in that direction, the wedging ball 21 adjacent the point |8| will not prevent such rotation. It is also apparent that as disc I8 is given its planetary motion, the balls 21 come Its center III must also This line H8 accordingly corre-' successively into action and successively drop out of action. For smooth driving effects, it is of course advisable that there be a sufficiently close angular spacing between these balls.

I claim:

1. In a device of the character described, a pair of members having respectively parallel, spaced axes, one of the axes being revoluble with respect to the other, said members being spaced in an axial direction, and means forming a driving connection between adjacent axially spaced sides of the members for revolving said one axis, the areas of contact between said means and at least one of said members being on planes that are substantially perpendicular to the axes.

2. In a device of the character described, a pair of members, one of said members having a pair of sections respectively disposed on opposite sides of the other member, means forming a driving connection between adjacent axially spaced sides, said sections being arranged, during operation, to exert equal and opposite thrusts on the intermediate members, said members having parallel axes, means for varying the spacing between the parallel axes, and means for optionally releasing and reestablishing said driving connection.

3. In a device of the character described, a pair of members having respectively parallel, spaced axes, one of the axes being revoluble with respect to the other, said members being spaced in an axial direction, and means forming a driving connection between adjacent axially spaced sides of the members for revolving said one axis, the areas of contact between said means and at least one of said members being on planes that are substantially perpendicular to the axes, and

means for varying the spacing between the axes.

4. In a device of the character described, a pair of members having respectively parallel spaced axes, one of the axes being revoluble with respect to the other, said members'being' spaced in an axial'direction, means forming a driving connection between adjacent axially spaced sides; the areas of contactbetween said means and at least one of said members b'ein'gon planes that are substantially perpendicular'to' the axes,

axes.

5; In a power transmission device, a pair of members having respectively parallel spaced .axes, one of the axes being revoluble with reand means for varying the spacing between" the V '7. In a power transmission device, a pair of members having spaced parallel axes, as well as adjacent side surfaces, one of the axes being revoluble with respect to the other, means for varying the spacing between the axes, and means forming a one-way drive between the members, including one or more roller members interposed between the surfaces.

8. In a power transmission device, a pair of members having spaced parallel axes, as well as adjacent side surfaces, one of the axes being revoluble with respect to the other, and means forming a one-way drive between the members, including one or more roller members interposed between the surfaces, and means for optionally varying the direction of the drive and for disconnecting the drive.

9. The combination as set forth in claim 8, in which the means for optionally varying the direction of the drive and for disconnecting the drive, comprises a shift member for moving the rolling members either to neutral or to engaging position with respect to the members.

10. In a device of the character described, a plate, a member disposed on one side of the plate and having a series of pockets with oppositely slanting surfaces to form in conjunction with the side of the plate, wedging spaces in both dim tions from the deep part of the pocket, a rolling wedge member in each pocket, means for shifting the wedge members optionally to the deep part of the pocket so as to be out of wedging relationship, or to either side.of the pocket, and means providing relative motion between said plate and member.

11. In a device of the character described, a plate, a member disposed on one side of the plate and having an axis as well as a series of surfaces forming wedging spaces with the side surface of the plate, rolling wedge members in said spaces, and means for moving said plate in an orbital path with respect to said axis.

12. In a device of the character described, a plate, a member disposed on one side of the plate and having an axis as well as a series of pockets with oppositely slanting surfaces to form in conjunction with the side of the plate, wedging spaces in both directions from the deep'part of the pocket, a rolling wedge member in each pocket, means for shifting the wedge members optionally to the deep part of the pocket so as to be out of wedging relationship, or to either side of the pocket, and means for moving said plate in an orbital path with respect to said axis.

13. In a device of the character described, a plate member, a cooperating member, said members having parallel, spaced axes, and arranged side by side, said cooperating member having a series of surfaces forming a series of wedging spaces with the side surface of the plate member, said wedging spaces being angularly disposed about the axis of the cooperating member, a rolling wedge member in each space, and means for moving one of the axes inan orbital path about the other axis.

14. In a device of the character described, a plate member, a cooperating member, said members having parallel, spaced axes, and arranged side by side, said cooperating member having a series of pockets with oppositely slanting surfaces to form in conjunction with the side of theplate member, wedging spaces in both directions from the deep part of the pocket, said pockets being angularly disposed about the axis of the cooperating member, a rolling wedge member in each pocket, means for shifting the wedge members optionally to the deep part of the pocket so as to be out of wedgin relationship, or to either side of the pocket, and means for moving one of the axes in an orbital path about the other axis.

15. In a device of the character described, a plate member, a cooperating member, said members having parallel, spaced axes, and arranged side by side, said cooperating member having a series of pockets with oppositely slanting surfaces to form in conjunction with the side of the plate member, wedging spaces in both directions from the deep part of the pocket, said pockets being angularly disposed about the axis of the cooperating member, a rolling wedge member in each pocket, means for shifting the wedge members optionallyto the deep part of the pocket so asto be out of wedging relationship, or to either side of the pocket, means for moving one of the axes in an orbital path about the other axes, and means for varying the distancebetween the axes.

16. In a device of the character described, a stationary member, a plurality of rolling elements annularly arranged in pockets in the side surface of said member, and forming a closely spaced series, a member having a free axis of rotation parallel to the center about which the pockets are arranged, means for imparting an orbital motion to said axis, each of said pockets having sides converging inwardly to form for the corresponding rolling element, a pair of wedging spaces, a spring barrier in the deep part of each pocket for yieldingly holding the corresponding rolling element in one or the other of the wedging spaces, and a shift device having projections entering between the rolling elements and angularly shiftable optionally to move all of the rolling elements simultaneously into either wedging space.

17. In a device of the character described, a pair of members having respectively parallel, spaced axes, one of the axes being revoluble with respect to the other, .said members being spaced in an axial direction, and means providing a and means whereby driving connection is maintained only on a restricted surface.

19. The combination as set forth in claim 18,

in which the means for maintaining driving connection only on a restricted surface, comprises a series of annularly spaced wedging rolling elements, disposed between the members, said series being spaced so closely so that as the revolving motion progresses, the surface of driving connection progresses in a c rresponding manner by shifting from one set 0 rolling elements to the next set.

20. In a device of the character described, a pair of members respectively having axes that are maintained parallel and sides that are axially spaced, means for adjusting the spacing of the axes, and means forming a driving connection between adjacent axially spaced sides of the members, comprising a plurality of rolling elements interposed between the members, one of said members having grooves for the accommodation of the rolling elements, said grooves having radial extensions to permit the elements to move radially toward and from the axis of said member, said grooves also having a wedging surface to cause the rolling element to be placed in operative relation to both said members.

gagement serving to define a circle on each of said members with respect to that members axis, said circles being of diiferent diameters,

characterized by the provision of means for so varying the relative positions of said axes that the diameter of one of said circles varies from less than the diameter of the other circle to greater than the diameter of the other circle.

STOV'ER C. WINGER. 

